CN104033299B - A kind of common-rail injector - Google Patents
A kind of common-rail injector Download PDFInfo
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- CN104033299B CN104033299B CN201410277034.5A CN201410277034A CN104033299B CN 104033299 B CN104033299 B CN 104033299B CN 201410277034 A CN201410277034 A CN 201410277034A CN 104033299 B CN104033299 B CN 104033299B
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- control piston
- orifice plate
- oil
- common
- plate bottom
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Abstract
The present invention has announced a kind of common-rail injector, it is characterized in that: control piston, oil injector body, orifice plate have formed control chamber. By appropriate design orifice plate bottom surface and control piston top shape, in the time of fuel injector oil spout, form throttling endless belt at control piston and orifice plate bottom surface, produce restriction effect, thereby significantly reduce the dynamic oil return of fuel injector, reduce fuel injector heating, reduced oil feed pump power loss. Simultaneously accurately restrictor ring band gap between design orifice plate bottom surface and control piston head, piston is risen completely after in complete quick condition. And then regulate the restrictor ring gap between control piston and orifice plate bottom surface by hydro-cushion automatic floating, thus the control chamber pressure gap causing because of rigging error restrictor ring band gap difference reduced, and then improve fuel injector assembling uniformity.
Description
Technical field
The invention belongs to internal combustion engine injection system field, relate to specifically a kind of common-rail injector.
Background technology
In order to meet the Abgasgesetz of increasingly stringent, the expulsion pressure of fuel system is more and more higher. Along with the raising of expulsion pressure, the dynamic oil return of fuel injector is also increasing. The dynamic recirculating oil quantity of fuel injector increases, and will increase the energy consumption of oil feed pump, reduces the economy of fuel system. Simultaneously more high pressure fuel leaks in low pressure oil way, will cause fuel injector mesolow oil circuit temperature higher, and then affect stability, the reliability of fuel injector work. In addition, from the operation principle of fuel injector, fuel injector is rising or the decline by controlling the fuel pressure in control chamber, thus the moving up and down vertically of the control piston by pressure differential control fuel oil injector. In the design of fuel injector in order to reduce the injection delay of fuel injector, can be by the design of fuel-displaced fuel injector metering-orifice and oil-feed metering-orifice flow-rate ratio larger. This makes the amplitude of intermediate fuel oil pressure decreased of control chamber larger, thereby cause in the time of end of injection, it is slower that the fuel pressure in control chamber recovers, and it is longer that fuel injector cuts out delay, cause fuel injector oil spout sensitivity variation, limited the raising of fuel injector multi-injection ability.
Summary of the invention
The object of the invention is to provide a kind of and when significantly reducing the dynamic oil return of fuel injector, reduces fuel injector and close delay by forming throttling endless belt at control piston and orifice plate bottom surface, having realized, and then improves fuel injector oil spout sensitivity.
The present invention for achieving the above object, adopts following technical scheme:
A kind of common-rail injector, comprises the control chamber being formed by control piston, oil injector body, orifice plate; Between control piston top and orifice plate bottom surface, form fit-up gap, between needle-valve top and oil injector body, form the spacing gap of needle-valve; Described orifice plate bottom surface is provided with the conduction hole communicating with fuel-displaced metering-orifice, and control chamber top is provided with oil-feed metering-orifice; It is characterized in that: in fuel injector injection process, after control piston rises, form throttling endless belt at control piston top and orifice plate bottom surface.
A kind of form: described control piston top is circular arc.
Described control piston top arc shape diameter is greater than 3 times of control piston diameter.
Another kind of form: described control piston top is trapezoidal.
The trapezoidal minor face in described control piston top is less than conduction hole diameter.
Between described control piston top and orifice plate bottom surface, fit-up gap is less than the spacing gap 0 ~ 0.02mm of needle-valve between needle-valve top and oil injector body.
Further: after control piston rises completely, to regulate the restrictor ring band gap between control piston and orifice plate bottom surface by hydro-cushion automatic floating.
Further: fuel-displaced metering-orifice and oil-feed metering-orifice flow-rate ratio are 1.3 ~ 1.8.
Good effect of the present invention is:
The present invention, by appropriate design orifice plate bottom surface and control piston top shape, in the time of fuel injector oil spout, forms throttling endless belt at control piston and orifice plate bottom surface, produce restriction effect, thereby significantly reduce the dynamic oil return of fuel injector, reduce fuel injector heating, reduced oil feed pump power loss. Simultaneously accurately restrictor ring band gap between design orifice plate bottom surface and control piston head, piston is risen completely after in complete quick condition. And then regulate the restrictor ring gap between control piston and orifice plate bottom surface by hydro-cushion automatic floating, thus the control chamber pressure gap causing because of rigging error restrictor ring band gap difference reduced, and then improve fuel injector assembling uniformity. Control chamber is because the acting in conjunction meeting of the throttling endless belt between fuel-displaced metering-orifice, control piston and orifice plate bottom surface makes control chamber keep higher pressure, after magnetic valve power-off, it is faster that control chamber pressure recovers, and it is shorter that delay is closed in oil spout, improved fuel injector oil spout sensitivity. Fuel-displaced metering-orifice and oil-feed metering-orifice flow-rate ratio can suitably increase, and close thereby reduce fuel injector the injection delay that delay reduces simultaneously.
Brief description of the drawings
Fig. 1 is structural representation of the present invention.
Fig. 2 control piston liter opens rear partial schematic diagram.
Fig. 3 restrictor ring band gap is on affecting dynamic oil return.
Fig. 4 restrictor ring band gap is closed delayed impact to oil spout.
In figure: 1-needle-valve; 2-needle-valve body; 3-adjustment block; The spacing gap of 4-needle-valve; 5-push rod; 6-oil injector body; 7-control piston; 8-fit-up gap; 9-conduction hole; The fuel-displaced metering-orifice of 10-; 11-orifice plate; 12-oil-feed metering-orifice; 13-control chamber; 14-high-pressure oil duct; 15-throttling endless belt.
Detailed description of the invention
A kind of common-rail injector of the present invention can be with reference to the description of accompanying drawing 1.
The control piston 7 of fuel injector, oil injector body 6, orifice plate 11 have formed control chamber 13. Fuel injector is rising or the decline by controlling the fuel pressure in control chamber 13, and then by pressure differential control control piston 7 moving up and down vertically, thereby control needle-valve 1 motion control injection process. By reducing fit-up gap 8 between control piston 7 tops and orifice plate 11 bottom surfaces, in the time of fuel injector oil spout, after control piston 7 rises, at the bottom of control piston 7 tops and orifice plate, between 11, form throttling endless belt 15, generation restriction effect has been realized and has significantly been reduced the dynamic oil return of fuel injector (as shown in Figure 3). In order to bring into play better the restriction effect in gap between control piston 7 tops and orifice plate 11, after avoiding control piston 7 to rise, block oil-feed metering-orifice 12,7, control piston top be circular arc or is trapezoidal, and arc diameter is greater than 3 times of control piston 7 diameters, and trapezoidal minor face is less than conduction hole 9 diameters.
From the operation principle of fuel injector, it is very large that performance impact is opened, closed to turnover metering-orifice flow-rate ratio to fuel injector. In the present invention, when fuel-displaced metering-orifice 10 is brought into play throttling action, between control piston 7 tops and orifice plate 11 bottom surfaces, also design throttling endless belt 15, performance throttling action, this will cause control chamber 13 to keep higher fuel pressure. After magnetic valve power-off, control chamber pressure is higher, its recovery will be faster, delay shorter (Fig. 4) is closed in oil spout, has improved fuel injector oil spout sensitivity. Like this can fuel-displaced fuel injector metering-orifice 10 is relative larger with the 12 flow-rate ratio designs of oil-feed metering-orifice at the design initial stage of fuel injector, rise to 1.3 ~ 1.8, when making fuel injector reduce to close delay, reduce to open delay.
The rule of the variation of control chamber 13 intermediate fuel oil pressure has determined the distributive value of fuel injector fuel oil, and from Fig. 3,4, between fuel injector control piston 7 tops and orifice plate 11 bottom surfaces, that dynamic recirculating oil quantity, oil spout are closed to delayed impact is very large in throttling endless belt gap. In order to reduce control chamber pressure 13 differences that cause because of rigging error throttling endless belt 15 gap differences, and then improve fuel injector assembling uniformity. Fit-up gap 8 between control piston top and orifice plate bottom surface is less than to the 0 ~ 0.02mm in the spacing gap 4 of needle-valve, after being risen completely, control piston 7 in complete quick condition, regulates throttling endless belt 15 gaps between control piston 7 and orifice plate 1 bottom surface by hydro-cushion automatic floating.
Claims (8)
1. a common-rail injector, comprises the control chamber being formed by control piston, oil injector body, orifice plate; Between control piston top and orifice plate bottom surface, form fit-up gap, between needle-valve top and oil injector body, form the spacing gap of needle-valve; Described orifice plate bottom surface is provided with the conduction hole communicating with fuel-displaced metering-orifice, and control chamber top is provided with oil-feed metering-orifice; It is characterized in that: in fuel injector injection process, after control piston rises, form throttling endless belt at control piston top and orifice plate bottom surface, produce restriction effect, thereby significantly reduce the dynamic oil return of fuel injector.
2. common-rail injector according to claim 1, is characterized in that: described control piston top is circular arc.
3. common-rail injector according to claim 2, is characterized in that: described control piston top arc shape diameter is greater than 3 times of control piston diameter.
4. common-rail injector according to claim 1, is characterized in that: described control piston top is trapezoidal.
5. common-rail injector according to claim 4, is characterized in that: the trapezoidal minor face in described control piston top is less than conduction hole diameter.
6. according to the common-rail injector described in claim 1-5 any one, it is characterized in that: between described control piston top and orifice plate bottom surface, fit-up gap is less than the spacing gap 0 ~ 0.02mm of needle-valve between needle-valve top and oil injector body.
7. common-rail injector according to claim 6, is characterized in that: after control piston rises completely, regulate the restrictor ring band gap between control piston and orifice plate bottom surface by hydro-cushion automatic floating.
8. common-rail injector according to claim 1, is characterized in that: fuel-displaced metering-orifice and oil-feed metering-orifice flow-rate ratio are 1.3 ~ 1.8.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410277034.5A CN104033299B (en) | 2014-06-19 | 2014-06-19 | A kind of common-rail injector |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410277034.5A CN104033299B (en) | 2014-06-19 | 2014-06-19 | A kind of common-rail injector |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104033299A CN104033299A (en) | 2014-09-10 |
| CN104033299B true CN104033299B (en) | 2016-05-11 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201410277034.5A Active CN104033299B (en) | 2014-06-19 | 2014-06-19 | A kind of common-rail injector |
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Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107061088B (en) * | 2016-12-12 | 2019-09-03 | 中国第一汽车股份有限公司 | A kind of New Common Rail fuel injector |
| CN106640452A (en) * | 2016-12-21 | 2017-05-10 | 安徽瑞沃电子科技有限公司 | Special oil injection device for highpressure common rail |
| CN106870230B (en) * | 2017-01-06 | 2019-09-24 | 中国第一汽车股份有限公司 | A kind of common-rail injector |
| CN107061091A (en) * | 2017-06-03 | 2017-08-18 | 成都威特电喷有限责任公司 | The piston component of adaptive equalization couple fit clearance circumferential weld deformation |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101331312A (en) * | 2005-12-12 | 2008-12-24 | 罗伯特·博世有限公司 | Fuel injector having a directly actuable injection valve element |
| CN102364080A (en) * | 2011-11-22 | 2012-02-29 | 哈尔滨工程大学 | Multistage throttling pressure-stabilizing electric control fuel injector |
| CN103104391A (en) * | 2013-02-05 | 2013-05-15 | 中国第一汽车股份有限公司无锡油泵油嘴研究所 | Electronic control diesel engine fuel injector with control valve |
| CN103216370A (en) * | 2008-01-23 | 2013-07-24 | 卡特彼勒公司 | Fuel injector and method of assembly therefor |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7331329B2 (en) * | 2002-07-15 | 2008-02-19 | Caterpillar Inc. | Fuel injector with directly controlled highly efficient nozzle assembly and fuel system using same |
| JP2013139712A (en) * | 2011-12-28 | 2013-07-18 | Nippon Soken Inc | Fuel injection valve |
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2014
- 2014-06-19 CN CN201410277034.5A patent/CN104033299B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101331312A (en) * | 2005-12-12 | 2008-12-24 | 罗伯特·博世有限公司 | Fuel injector having a directly actuable injection valve element |
| CN103216370A (en) * | 2008-01-23 | 2013-07-24 | 卡特彼勒公司 | Fuel injector and method of assembly therefor |
| CN102364080A (en) * | 2011-11-22 | 2012-02-29 | 哈尔滨工程大学 | Multistage throttling pressure-stabilizing electric control fuel injector |
| CN103104391A (en) * | 2013-02-05 | 2013-05-15 | 中国第一汽车股份有限公司无锡油泵油嘴研究所 | Electronic control diesel engine fuel injector with control valve |
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| CN104033299A (en) | 2014-09-10 |
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